WO2015018583A1 - Machine à plateau oscillant utilisée comme pompe à pistons axiax et/ou comme moteur à pistons axiaux - Google Patents

Machine à plateau oscillant utilisée comme pompe à pistons axiax et/ou comme moteur à pistons axiaux Download PDF

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Publication number
WO2015018583A1
WO2015018583A1 PCT/EP2014/064537 EP2014064537W WO2015018583A1 WO 2015018583 A1 WO2015018583 A1 WO 2015018583A1 EP 2014064537 W EP2014064537 W EP 2014064537W WO 2015018583 A1 WO2015018583 A1 WO 2015018583A1
Authority
WO
WIPO (PCT)
Prior art keywords
hydraulic fluid
seal
bearing
swash plate
drive shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2014/064537
Other languages
German (de)
English (en)
Inventor
Eberhard Maier
Matthias Greiner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of WO2015018583A1 publication Critical patent/WO2015018583A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F03C1/0644—Component parts
    • F03C1/0663—Casings, housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2064—Housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18—Lubricating

Definitions

  • the present invention relates to a swash plate machine according to the preamble of claim 1, a method for operating a
  • Swash plate machines serve as axial piston pumps for converting mechanical energy into hydraulic energy and as axial piston motor for converting hydraulic energy into mechanical energy.
  • Cylinder drum with piston bores is rotatably or rotatably mounted and pistons are arranged in the piston bores.
  • the cylinder drum is fixedly connected to a drive shaft and a hydraulic fluid acts temporarily on a first part of the rotating piston bores under high pressure and a hydraulic fluid acts temporarily on a second part of the rotating piston bores at low pressure.
  • a pivoting cradle is around one
  • Swivel axis mounted pivotably and on the pivoting cradle is on a retaining disc with sliding shoes.
  • the pistons are attached to the sliding shoes.
  • the retaining disc with the sliding shoes together with the cylinder drum rotates about an axis of rotation and a flat bearing surface of the pivoting cradle is at an acute angle, for example between 0 ° and + 20 ° and between 0 ° and -20 ° as a swivel angle aligned with the axis of rotation of the cylinder drum.
  • the sliding blocks are mounted with a sliding bearing, which is generally hydrostatically relieved, on the support surface of the pivoting cradle and the sliding blocks are connected to the retaining disc.
  • the swing cradle is powered by two hydraulic Swiveling devices, each of an adjusting piston and a
  • Adjusting cylinders are formed, pivoted about a pivot axis.
  • a housing encloses an interior of the swash plate machine and within the housing, the components of the swash plate machine are arranged. The interior is filled with hydraulic fluid.
  • the drive shaft is guided through an opening of the housing to the outside of the interior, so that a torque can be delivered or absorbed by the drive shaft.
  • On the housing a seal is attached, which seals the rotating drive shaft liquid-tight, so that no hydraulic fluid can flow from the interior to the outside. Frictional forces occur, for example, between a rotating and a stationary sliding ring on the seal, and these frictional forces lead to heating and thus increased wear of the two sliding rings. As a result, disadvantageously, the
  • Gasket has a short life and must be replaced if necessary in a complex manner to the functioning of the
  • EP 1 013 928 A2 shows an axial piston pump in a swashplate design with a driven circumferential and a plurality of piston bores having cylinder bores, wherein in each separated by webs piston bores are arranged linearly between a bottom dead center and a top dead center pistons and a low pressure connection kidney and a Hochdruckin kidney having control disk is provided.
  • the CH 405 934 shows a Schrägusionnaxialkolbenpumpe whose non-rotating cylinder block for varying the flow rate in dependence on the delivery pressure is longitudinally displaceable, wherein at the pressed by a spring in the direction of increasing the delivery cylinder block a
  • Control slide unit is attached with a spool.
  • DE 27 33 870 C2 shows a control device for a
  • Oblique disk axial piston pump on each side of the cradle for pivoting the swash plate, each a hydraulically acted upon
  • both motors by means of a pivotable about the pivot axis of the cradle arranged plate-shaped Control valve spool are controllable and are used to adjust the flow rate of the pump.
  • Swash plate machine as axial piston pump and / or axial piston motor, comprising one rotatable about an axis of rotation or
  • Piston bores movably mounted piston a housing which defines a filled with hydraulic fluid interior of the swash plate machine, at least rotatably connected to the cylinder drum drive shaft, which is formed inside and outside the interior, at least one bearing for the drive shaft, a seal for sealing by the Housing guided drive shaft to prevent leakage of hydraulic fluid from the interior, wherein a support for the drive shaft has a conveying action for hydraulic fluid and the storage with the conveying effect in a fluid-conducting connection with a
  • Hydraulic fluid filled edge space is at the seal, so that by means of the hydraulic fluid conveyed by the storage, the seal with the conveyed hydraulic fluid is coolable.
  • the storage for the drive shaft with the conveying action has to the seal a smaller distance than a further support for the drive shaft. Due to the promotion effect of
  • At least one inlet channel for guiding hydraulic fluid from a core space to the edge space is formed on the seal on the swash plate machine and / or at least one drain channel for conducting hydraulic fluid from the swash plate machine
  • Hydraulic fluid can be directed to the edge space for optimized cooling.
  • the swash plate machine has a plurality of inlet channels, which are formed tangentially in the region of the seal and / or the swash plate machine has several
  • Drain channels which are formed tangentially circumferentially in the region of the seal and / or the at least one inlet channel and / or the at least one drain channel is formed as a bore in the housing.
  • Hydraulic fluid are passed at several points in the edge space on the seal, as the multiple inlet channels and / or drainage channels are distributed tangentially circumferentially on the edge space. As a result, substantially uniform cooling by means of the delivered hydraulic fluid can be achieved on the seal due to a multiplicity of inlet channels and / or outlet channels.
  • the bearing with the conveying action for hydraulic fluid with the at least one flow channel fluidly connected in a supplementary embodiment, the bearing with the conveying action for hydraulic fluid with the at least one flow channel fluidly connected.
  • the bearing for the drive shaft with the conveying action for hydraulic fluid as a rolling bearing, in particular a simple
  • Tapered roller bearing, a spherical roller bearing or a double tapered roller bearing, trained and / or limited by the housing interior is filled with hydraulic fluid and the interior is divided into a fictional edge space and a fictitious core space and the edge space is at a distance from less than 5 cm, 3 cm or 1 cm to the seal on and the core space is formed by the interior without the edge space and / or with the
  • the seal is designed as a mechanical seal with a rotating seal ring and a stationary seal ring and the rotating seal ring rests on the stationary seal ring on a sealing gap and
  • Hydraulic fluid is due to the marginal space, especially in the area of
  • the seal is designed as a radial shaft seal with a resting on the rotating drive shaft fixed sealing ring, so that between the sealing ring and the drive shaft, a sealing gap is formed and hydraulic fluid through the edge space, in particular in the region of the sealing gap, on the fixed sealing ring and the rotating one
  • a swashplate machine comprising the steps of: introducing and discharging hydraulic fluid into piston bores on a rotating cylinder drum, moving pistons in the piston bores, supporting a rotating drive shaft from a bearing, sealing the rotary drive shaft with a seal, and discharging hydraulic fluid one
  • the hydraulic fluid is conveyed through at least one inlet channel from the core space to the edge space at the seal, and then the hydraulic fluid is conveyed through at least one drainage channel from the edge space at the seal to the core space.
  • Inventive drive train for a motor vehicle comprising at least one swash plate machine for converting mechanical energy into hydraulic energy and vice versa, at least one pressure accumulator, wherein the swash plate machine as one in this patent application
  • the drive train comprises two swash plate machines, which are hydraulically connected to each other and act as a hydraulic transmission and / or the drive train comprises two pressure accumulator as
  • the swash plate machine comprises a weighing storage for the pivoting cradle.
  • the swash plate machine comprises at least one
  • Swivel device for pivoting the swivel cradle.
  • the swashplate machine comprises a pivoting cradle mounted pivotably about a pivot axis with a support surface for supporting the pistons on the support surface.
  • the drive shaft about an axis of rotation, in particular the axis of rotation of the cylinder drum, rotatably or rotatably mounted.
  • the swash plate machine comprises a
  • Low-pressure opening for introducing and / or discharging hydraulic fluid into and / or out of the rotating piston bores.
  • the swash plate machine includes a high pressure port for discharging and / or introducing hydraulic fluid from and / or into the rotating piston bores.
  • 1 is a longitudinal section of a swash plate machine
  • Fig. 2 shows a cross section A-A of FIG. 1 a valve disc of
  • FIG. 3 is a partial longitudinal section of the swash plate machine with a seal in a first embodiment and a storage in a first embodiment
  • Fig. 6 is a partial longitudinal section of the swash plate machine with the seal in a second embodiment and the storage in the first embodiment and
  • FIG. 7 shows a drive train for a motor vehicle.
  • a swashplate machine 1 shown in a longitudinal section in FIG. 1 serves as an axial piston pump 2 for converting or converting mechanical energy (torque, rotational speed) into hydraulic energy (volumetric flow, pressure). or as an axial piston motor 3 for the conversion or conversion of hydraulic energy (volume flow, pressure) into mechanical energy (torque,
  • a drive shaft 9 is by means of a bearing 10 at a
  • Cylinder drum 5 rotationally fixed and connected in the axial direction, wherein the drive shaft 9 and the cylinder drum 5 are formed in one or two parts and the boundary between the drive shaft 9 and the cylinder barrel 5 is shown in Fig. 1 by dashed lines.
  • the cylinder drum 5 performs the rotational movement of the
  • Cylinder drum 5 a plurality of piston bores 6 with an arbitrary cross-section, for example square or circular, incorporated.
  • the longitudinal axes of the piston bores 6 are substantially parallel to the axis of rotation 8 of the drive shaft 9 or the cylinder drum 5
  • a pivoting cradle 14 is mounted pivotably about a pivot axis 15 on the housing 4. The pivot axis 15 is perpendicular to the
  • the axis of rotation 8 of the cylinder drum 5 is arranged parallel to and in the plane of the drawing of FIG. 1 and perpendicular to the plane of the drawing of FIG. 2.
  • the housing 4 is liquid-tightly bounded by an interior space 44 which is filled with hydraulic fluid.
  • the pivoting cradle 14 has a flat or planar support surface 18 for the indirect support of a retaining disk 37 and for the direct support of sliding shoes 39.
  • the retaining disc 37 is provided with a plurality of sliding shoes 39 and each sliding block 39 is connected to a respective piston 7.
  • the sliding block 39 on a bearing ball 40 (Fig. 1) which is fixed in a bearing cup 59 on the piston 7, so that a
  • Piston joint 22 between the bearing ball 40 and the bearing cup 59 is formed on the piston 7.
  • Bearing ball 40 and bearing cup 59 are both complementary or spherical, thereby characterized in a corresponding movement possibility to each other between the bearing ball 40 and the bearing cup 59 to the piston
  • Sliding shoes 39 perform the sliding blocks 39 a rotational movement about the rotation axis 8 with and due to the fixed connection or arrangement of the sliding shoes 39 on the retaining disc 37 also performs the retaining disc
  • the pivoting cradle 14 is - as already mentioned - pivotally mounted about the pivot axis 15 and further comprises an opening 42 (Fig. 1) for
  • a weighing storage 20 is formed on the housing 4.
  • 14 two bearing sections are formed on the pivoting cradle.
  • the two bearing sections of the pivoting cradle 14 lie on the
  • the pivoting cradle 14 is thus by means of a
  • Swivel axis 15 pivotally mounted.
  • the support surface 18 according to the sectional formation in Fig. 1 has a pivot angle ⁇ of approximately + 20 °.
  • the pivot angle ⁇ is present between a fictitious plane perpendicular to the axis of rotation 8 and a plane spanned by the flat bearing surface 18 of the pivoting cradle 14 according to the
  • the pivoting cradle 14 can between two pivotal limit angle ⁇ between + 20 ° and -20 ° by means of two
  • Swivel devices 24 are pivoted.
  • the first and second pivoting means 25, 26 as pivoting means 24 has a connection point 32 between the pivoting device 24 and the pivoting cradle 14.
  • the two pivoting devices 24 each have an adjusting piston 29, which is movably mounted in an adjusting cylinder 30.
  • the adjusting piston 29 or an axis of the adjusting cylinder 30 is aligned substantially parallel to the axis of rotation 8 of the cylinder drum 5.
  • Adjusting piston 29 has this a bearing cup 31, in which a
  • Bearing ball 19 is mounted.
  • FIG. 1 (Fig. 1 to 2) of the pivoting cradle 14 is present.
  • the first and second Pivoting device 25, 26 is thus connected to a respective pivot ball 19 on a respective pivot arm 16 with the pivoting cradle 14.
  • the pivoting cradle 14 can be pivoted about the pivot axis 15, as a result Adjustment piston 29 to the open valve 27, 28 with a hydraulic fluid under pressure in the adjusting cylinder 30, a force is applied.
  • a valve disk 1 1 is located on the end of the cylinder drum 5 shown on the right in FIG. 1, with a kidney-shaped high-pressure opening 12 and a kidney-shaped
  • the piston bores 6 of the rotating cylinder drum 5 are thus fluidly connected in an arrangement on the high-pressure opening 12 with the high-pressure opening 12 and in an arrangement on the
  • Low-pressure port 13 fluidly connected to the low pressure port 13. At a swivel angle ⁇ of 0 ° and during operation of the
  • Axial piston motor 3 have the piston bores 6, which are temporarily in fluid-conducting connection with the high-pressure opening 12, have a greater pressure on hydraulic fluid than the piston bores 6, which are temporarily in fluid-conducting connection with the low-pressure opening 13.
  • An axial end 66 of the cylinder drum 5 rests on the valve disc 1 1.
  • a second side 65 has a Recess for supporting the drive shaft 9 with a further storage 10.
  • the drive shaft 9 is guided through the opening 63, so that the
  • Drive shaft 9 is formed integrally inside and outside of the inner space 44.
  • Fig. 3 is a partial longitudinal section of a first embodiment of the
  • Tapered roller bearing 43 has rollers 68 as rolling elements 67, which rest on an inner ring 69 and an outer ring 70.
  • a seal 80 is formed in the region of the simple tapered roller bearing 43 to prevent leakage of the hydraulic fluid from within the inner space 44 in the region of
  • the seal 80 is formed as a mechanical seal 71. A rotating one
  • Seal housing ring 78 is fixedly connected to the drive shaft 9 and to the rotating seal housing ring 78, a rotating seal ring 72 is attached from an elastic material.
  • a fixed seal housing ring 79 is fixedly secured to the flange 21 of the housing 4, and on the stationary seal housing ring 79 is a fixed sliding ring 73 of a
  • the housing 4 defines the interior 44, which is filled with hydraulic fluid and also receives components of the swash plate machine 1.
  • the inner space 44 is subdivided into a fictional edge space 17 with a distance of less than 2 cm from the mechanical seal 71 and into a fictitious core space 23.
  • the fictitious core space 23 represents the entire inner space 44 minus the marginal space 17 on the flange 21 designed as a bore 35 inlet channel 33 is incorporated.
  • Outer ring 70 serves to receive the rollers 68 and also additionally forms a drainage channel 34 for hydraulic fluid.
  • the drainage channel 34 is in particular between the inner and outer ring 69, 70 and outside the
  • the simple tapered roller bearing 43 has a Pumping action for hydraulic fluid, ie forms a pump for conveying the hydraulic fluid. Due to the fluid-conducting connection of the marginal space 17 by means of the inlet and outlet channels 33, 34 can be promoted during operation of the swash plate machine 1, ie at a rotating drive shaft 9 of the simple tapered roller bearing 43 hydraulic fluid, ie from the core chamber 23 through the inlet channel 33 to the edge space 17 be promoted in the region of the mechanical seal 71 and then transported back from the edge space 17 through the drain passage 34 into the core chamber 23 back as a circuit.
  • Hydraulic fluid is thereby conveyed through the marginal space 17 with the very small distance to the mechanical seal 71, so that the mechanical seal 71, ie the rotating and fixed sliding ring 72, 73, can be advantageously cooled by means of the conveyed hydraulic fluid.
  • a second embodiment of the rolling bearing 36 is shown.
  • Rolling bearing 36 is formed as a spherical roller 61.
  • the drainage channel 34 is formed both between the inner and outer ring 69, 70 of the spherical roller bearing 61 and in addition as a bore 35 in the flange 21 of the housing 4th
  • a third embodiment of the rolling bearing 36 is shown.
  • the rolling bearing 36 is formed as a double tapered roller bearing 62 and the drain passage 34 is adjacent to the
  • Tapered roller bearing 62 also as a bore 35 on the flange 21 of the
  • Housing 4 is formed. 6, a second embodiment of the seal 80 is shown.
  • Seal 80 is a radial shaft seal 75 with an elastic
  • Hose spring 77 is fixed to the flange 21 of the housing 4 and on the annular tube spring 77 of the elastic sealing ring 76 is attached.
  • the elastic sealing ring 76 rests on the outside on the rotating drive shaft 9, so that thereby the sealing gap 74 between the rotating outer surface the drive shaft 9 and the sealing ring 76 is formed.
  • the rolling bearing 36 is, as in the embodiment shown in Fig. 3, as a simple
  • Tapered roller bearing 43 is formed.
  • the mode of operation corresponds in an analogous manner to the embodiment shown in FIG. 3, d. H. from the simple tapered roller bearing 43 with the pumping action, the hydraulic fluid from the
  • Core space 23 through the inlet channel 33 to the flange 21 of the housing 4 to the edge space 17 is passed to cool the radial shaft seal 75 and then through the drain passage 34 between the inner and
  • Hydraulic fluid is present, which is formed or aligned by the core chamber 23 in the edge space 17 and vice versa.
  • Drive train 45 has an internal combustion engine 46, which drives a planetary gear 48 by means of a shaft 47.
  • Planetary gear 48 two shafts 47 are driven, wherein a first shaft 47 is connected to a clutch 49 with a differential gear 56.
  • a second or other shaft, which is driven by the planetary gear 48 drives a first swash plate machine 50 through a clutch 49 and the first swash plate machine 50 is hydraulically connected by means of two hydraulic lines 52 with a second swash plate machine 51.
  • the first and second swash plate machines 50, 51 thereby form a hydraulic gear 60, and from the second swash plate machine 51, the differential gear 56 can also be driven by means of a shaft 47.
  • Differential gear 56 drives the wheels 57 with the wheel shafts 58.
  • the drive train 45 has two pressure accumulators 53 as a high-pressure accumulator 54 and as a low-pressure accumulator 55.
  • the two accumulators 53 are hydraulically connected by means not shown hydraulic lines with the two swash plate machines 50, 51, thereby mechanical energy of the
  • Internal combustion engine 46 can be hydraulically stored in the high pressure accumulator 54 and also in a recuperation of a motor vehicle with the drive train 45 also kinetic energy of the motor vehicle in the high pressure accumulator 54 can be stored hydraulically.
  • By means of the hydraulic energy stored in the high-pressure accumulator 54 can with a Swash plate machine 50, 51 additionally the differential gear 56 are driven.
  • the rolling bearing 36 has a conveying action for hydraulic fluid, d. H. also forms a pump for conveying hydraulic fluid.
  • Seal 80 are led to cool the seal 80.
  • this can reduce the friction resulting from the heating of the seal 80 and the life and reliability of the seal 80 can be substantially increased.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne une machine à plateau oscillant (1) utilisée comme pompe à pistons axiaux (2) et/ou comme moteur à pistons axiaux (3) et comportant un tambour cylindrique (5) pourvu d'alésages de piston (6) et monté à rotation ou à pivotement autour d'un axe de rotation (8), des pistons (7) montés de manière mobile dans les alésages de piston (6), un boîtier (4) qui définit un espace intérieur (44) de la machine à plateau oscillant (1) qui est rempli de liquide hydraulique, un arbre d'entraînement (9) qui est relié au moins solidairement en rotation au tambour cylindrique (5) et qui est configuré à l'intérieur et à l'extérieur de l'espace intérieur (44), au moins un palier (10) destiné à l'arbre d'entraînement (9), un joint d'étanchéité (80) servant à réaliser l'étanchéité de l'arbre d'entraînement (9), guidé dans le boîtier (4), afin d'empêcher le liquide hydraulique de sortir de l'espace intérieur (44). Un palier (10) destiné à l'arbre d'entraînement (9) présente une action d'acheminement du fluide hydraulique et le palier (10) présentant l'action d'acheminement est, au niveau du joint d'étanchéité (80), en communication fluidique avec un espace en bordure rempli de liquide hydraulique de sorte que, grâce au liquide hydraulique acheminé par le palier (10), le joint d'étanchéité (80) peut être refroidi au moyen du fluide hydraulique acheminé.
PCT/EP2014/064537 2013-08-08 2014-07-08 Machine à plateau oscillant utilisée comme pompe à pistons axiax et/ou comme moteur à pistons axiaux Ceased WO2015018583A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013215680.4 2013-08-08
DE201310215680 DE102013215680A1 (de) 2013-08-08 2013-08-08 Schrägscheibenmaschine

Publications (1)

Publication Number Publication Date
WO2015018583A1 true WO2015018583A1 (fr) 2015-02-12

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PCT/EP2014/064537 Ceased WO2015018583A1 (fr) 2013-08-08 2014-07-08 Machine à plateau oscillant utilisée comme pompe à pistons axiax et/ou comme moteur à pistons axiaux

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WO (1) WO2015018583A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1802983A1 (de) * 1967-11-22 1969-06-19 Von Roll Ag Hydroaggregat
DE4010550A1 (de) * 1989-04-05 1990-10-11 Zahnradfabrik Friedrichshafen Axialkolbenpumpe
DE19613609A1 (de) * 1996-04-04 1997-10-09 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit internem Spülkreislauf
EP1022462A1 (fr) * 1999-01-22 2000-07-26 Brueninghaus Hydromatik Gmbh Machine hydraulique, notamment machine à piston, comportant un carter dans lequel est disposé une cloison de séparation
EP1050680A2 (fr) * 1999-05-07 2000-11-08 Brueninghaus Hydromatik Gmbh Joint d'arbre pour machine hydraulique
EP2362122A2 (fr) * 2010-02-24 2011-08-31 KSB Aktiengesellschaft Bague d'étanchéité glissante et procédé d'optimisation de leur comportement en fonctionnement

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH405934A (de) 1962-07-26 1966-01-15 Weatherhead Co Schrägscheiben-Axialkolbenpumpe
US4076459A (en) 1976-09-14 1978-02-28 Abex Corporation Horsepower limiter control for a variable displacement pump
EP1013928A3 (fr) 1998-12-22 2000-11-08 Parker Hannifin GmbH Pompe à pistons axiaux à plateau en biais avec disposif d'amortissement de pulsation

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1802983A1 (de) * 1967-11-22 1969-06-19 Von Roll Ag Hydroaggregat
DE4010550A1 (de) * 1989-04-05 1990-10-11 Zahnradfabrik Friedrichshafen Axialkolbenpumpe
DE19613609A1 (de) * 1996-04-04 1997-10-09 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit internem Spülkreislauf
EP1022462A1 (fr) * 1999-01-22 2000-07-26 Brueninghaus Hydromatik Gmbh Machine hydraulique, notamment machine à piston, comportant un carter dans lequel est disposé une cloison de séparation
EP1050680A2 (fr) * 1999-05-07 2000-11-08 Brueninghaus Hydromatik Gmbh Joint d'arbre pour machine hydraulique
EP2362122A2 (fr) * 2010-02-24 2011-08-31 KSB Aktiengesellschaft Bague d'étanchéité glissante et procédé d'optimisation de leur comportement en fonctionnement

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